Sonic pump



Sept. 3, 1963 A. G. BODINE, JR

SONIC PUMP 6 Sheets-Sheet 1 Filed April 28, 1961 ik K ATTORNEYS Sept. 3, 1963 A. G. BQODINE, JR

SONIC PUMP 6 SheetsSh eet 2 Filed April 28, 1961 'INVENTOR.

ALBERT G. BODINE JR;

H ATTORNEYS Sept. 3, 1963 A. G. BODINE, JR

some PUMP 6 Sheets-Sheet 3 Filed April 28. 1961 INVENTOR.

ALBERT G. BODINE JR. BY

ATTORNEYS Sept. 3, 1963 Filed April 28, 1961 FIG. 7

'llla' A. G. BODINE, JR

SONIC PUMP 6 Sheets-Sheet 4 FIG.8

PIC-3.9

INVENTOR.

ALBERT G. BODINE JR.

ATTORNEYS Sept. 3, 1963 SONIC PUMP Filed April 28. 1961 2|s FIG.

A. G. BODINE, JR

6 Sheets-Sheet 5 FIG. IO

INVENTOR.

ALBERT G. BODINE JR.

"ZWM

ATTORNEYS P 1963 A. G. BODINEQJR 3,102,482

some PUMP Filed April 28, 1961 6 Sheets-Sheet 6 FIG. l2

GROUND SURFACE FIG. l5

INERTIA REFLECTOR FIG. 14

INERTIA V REFLECTOR INVENTOR.

ALBERT G. BODINE JR.

Z /MW ATTORN EYS United States Patent Ofice 3,102,482 Patented Sept. 3, 1963 3,102,482 SQNIQ PUMP Albert G. Bodine, in, Los Angeles, Calif. (13120 Moorpark Sh, Sherman Oaks, Calif.) Filed Apr. 23, 1961, Ser. No. 106,394 14 Claims. (Cl. 103-4) This invention relates generally to deep well pumps of the sonic class, operating by virtue of elastic vibrations in an elastic wave transmission medium, as broadly exemplified, in a form utilizing longitudinally oriented vibrations, in my prior Patent No. 2,444,912, and in a form utilizing torsionally oriented vibrations, in my copending application Serial Number 815,510, filed May 5, 1959, entitled Method and Apparatus for Pumping Fluids by Oscillatory Impeller Action. The advantages of these sonic pumps are known and need not be dwelt upon herein.

In my prior sonic pumps, the driving energy is transmitted to the bottom of the well by an elastic wave in either the pump tubing, or a rod string extending through the pump tubing. Often, the frequency is so adjusted as to establish a standing wave in the tubing, characterized by alternating mtinodes and nodes or pseudo-nodes. The energy so transmitted down the well is utilized to motivate a vibratory fluid impelling means of the pump. The principal disadvantage of the sonic pumping system in this form is that the wave, transmitted from the ground surface to the bottom of the well, is subjected to a certain degree of attenuation which can be fairly appreciable when the well is deep. Moreover, the nodes are more pronounced the greater the distance from the oscillator, which is a disadvantage in that vibratory fluid impelling means located close to pronounced nodes are of little benefit. Vibration amplitude in the wave transmission medium at the bottom of the well is thus reduced, and the consequence is that the vibration amplitude of the fluid impelling means is correspondingly reduced, with consequent reduction in pumping rate below the maximum otherwise obtainable.

It is, accordingly, an object of the present invention to provide a sonic pump which avoids transmission of energy from the ground surface down to the region of the vibratory fluid impelling means in the form of an elastic wave, and wherein the elastic wave motion is generated downhole, and is there coupled or applied to the vibratory fluid impel-ling means. i

In accordance with the invention, motivating energy is transmitted down the well by means other than sonic elastic waves. For example, I may utilize a rotating column, such as a tubing or a shaft, the lower end of which drives a sonic vibration generator or oscillator located down in the well. Or, in another form of the invention, I may utilize a d-ownhole electric drivemotor, mechanic-ally coupled to the downhole vibration generator or oscillator. Electric power is transmitted to the motor through a conventional electric cable reaching from the ground surface. The oscillator, typically a longitudinal vibration generator, or a torsional vibration generator, then drives a vibratory fluid impelling means which operates in response to cyclic vibratory drive. In the case of a longitudinal vibration generator, this fluid impelling means may, if desired, be such as shown in my prior patent mentioned above or in any other of my prior patents on sonic pumps; and in the case of a torsional vibration generator, may be any of the types taught in my aforementioned application Serial No. 815,- 510, or any suitable substitute. 7

The invention will be better understood by referring .now to the following detailed description of two present illustrative embodiments thereof, reference for this purpose being bad to the accompanying drawings, in which:

FIG. 1 is a view, with longitudinal sections broken away, of a torsional type of sonic pumping installation in accordance with the present invention;

FIG. 2 is a view similar to portions of FIG. 1, to a larger scale, and showing only the upper and lower end portions of the pump installation, these portions being shown in longitudinal section;

FIG. 3 is a section taken on line 3-3 of FIG. 2;

FIG. 4 is a section taken on line 44 of FIG. 2;

FIG. 4a is a somewhat diagrammatic view of the rotors, showing a position thereof 90 beyond that of FIG. 4, and showing force components thereon;

FIG. 5 is a view similar to FIG. 1, but showing a modified form of pump;

FIG. 6 is a view similar to FIG. 2, but showing the pump of FIG. 5;

1G. 7 is a view similar to FIG. 1, but showing another modification of the pump;

FIG. 8 is an enlarged sectional detail of a portion of FIG. 7;

FIG. 9 is a view similar to FIG. 8 but showing another modification of the pump;

FIG. 10 is a view similar to FIG. 1 but showing still another modification of the pump;

FIG. 11 is a view similar to FIG. 2, but showing the pump of FIG. 10;

FIG. d2 is a standing wave diagram typical of sonic pumps as heretofore known;

FIG. 13 is a standing wave diagram typical of one class of sonic pumps in accordance with the invention;

FIG. 14 shows a modification of 'FIG. 13, obtained by use of a wave reflector at a quarter wave length distance up the elastic column member from the lower end; and

FIG. 15 shows a modification in which the wave reflector is located an odd number of quarter wave lengths (more than one) up the column [from the lower end.

In FIGS. 1-4 of the drawings, numeral 10 designates generally a well casing extending from the ground surface down into the earth to the location of the productive formation 11, and this casing has, in its lower end region, usual perforations or inlet openings 12 for petroleum or other well liquids. Casing 19 has at the top a casing head 13, which supports a rotary conical roller type bearing means indicated generally at 14, the inner race ring 15 of which embraces tubing string 16 and engages under a collar v17 secured to the latter. The outer race ring is seated in the casing head, as shown. Pumping tubing 16 is thus both rotatably and vertically supported by bearing 14 carried by casing head 13. Means are provided for constantly rotating pump string 16, which functions as a mechanical powertransmission means; and as here shown, collar 17 is, to this end, provided with a pulley 18 connected by a belt 19 with a pulley 2d driven by an electric drive motor 21. Any other convenient means may of course be provided for rotating the pump string.

The upper extremity '22 of pump tubing 16 is swivelled, as at 2.3,and sealed, as at 24, within an L-fitting 25, threaded as at 26 for connection to a delivery line, not shown.

Coupled to the lower end of pump tubing 16, in the bottom of the well, is a torsionally vibratory fluid imelling means 3b, which may be such as shown in several forms in my aforementioned application Serial .No.

815,510, one illustrative example of which is shown herein in FIG. 3. The threaded lower end of the lowermost tubing stand 1-6 is screwed into the upper end of coupling collar 31, and into the lower end of coupling collar 31 is screwed a tubular, terminally threaded tubular upper end portion 32 of an axial shaft 33 of torsion oscillator or generator 34.

or suitable plastic, such as nylon, Teflon, etc.

Considering the torsional fluid impelling unit 3% in more particular, and referring to FIG. 3, a cylindrical body 38, of lesser diameter than the interior diameter of tubing 16, has at its lower end a reduced stem 39, from the lower extremity of which project a plurality of lugs 40 which seat on the upper end of tubular member 32 and are retained thereagainst by means of a coil compression spring4l engaging the lower end of tubing 16. Mounted on cylindrical body 38 are a plurality of flexible vanes 43-, arranged as indicated in the drawings. The lower ends of these vanes have hubs 4A fitted tightly on pins 45 'set tightly in cylindrical body 38. The vanes are preferably flexible, and may be composed of rubber Assuming torsional oscillation of the assembly, the vanes, acting against fluids in the space surrounding them, propel the fluid in an upward direction, all as more. particularly described in my aforementioned earlier application Serial No. 815,510;

Additional fluid impelling units 3t? are coupled into the tubing string at vertically spaced points therein, depending upon local conditions, such as depth of the well, production volume, etc. They are best located at velocity antinodes in the tubing, to be explained later.

The aforementioned shaft 33 of torsion oscillator 34 has, near its upper end, an annular outwardly extending flange 50, and spaced therebelow, at its lower extremity, another annular outwardly extending flange 51, so as to form a spool-like structure 52. Rotatably and vertically supported by means of a thrust bearing 53 mounted on shaft 33 just above flange S is the upper end wall 54 of a cylindrical housing 55 that surrounds the spool structure 52. The housing 55 is completed by cylindrical sidewall 56 and lower end wall 57.

An annular body 58 extending downwardly from bottorn housing wall 57 provides support for a plurality of bow spring anchors 59 which frictionally'engage casing 10, so as to resist rotation of housing 55. This body 58 also contributes substantial inertia, also serving to resist rotation.

Mounted on lower housing wall 57 andfixed thereto is a stationary sun gear 60, and meshing therewith are planet gears 61. In this example, there are four of the planet gears 61, disposed 90 apart. The planet gears 61 are fixed on the lower ends of shaft portions 62 journalled in lower spool flange 51 as by bearings 63. These shaft portions 62 are on the lower ends of cranklike unbalanced rotors 64 whose upper extremities have similar shaft portions 65 journalled in bearings 66 set into upper spool flange 50. These crank-like rotors 64 afford eccentric masses 67 adapted, when rotated relatively to spool 52, to exert torsional reactions thereon, as will be explained in more particular below. Extending upwardly from sun gear as is a pin 68 supporting a bearing 69 set into the lower end of the spool thus providing for journalling of the lower end of the spool within housing 55.

Operation is as follows: The pump tubing string 16 is continuously rotated by means described above. Continuous rotation is thereby imparted to shaft 33 and spool 52. Housing 55 surrounding the spool, however, is held against rotation by how spring anchors 59', the inertia of body 58, or other anchoring means found suitable to the purpose. Planet gears 61, accordingly, planetate about stationary sun gear 60, turning on their own axes a number of times for each circuit around the sun gear.

' The eccentrically weighted rotors 64, accordingly, turn constantly on the axes of gears m, as a frequency multiplied over that of the spool and pipe string. For example, the multiplying ratio may be something of the order of 3.1 to l, or considerably higher, if desired, and a suitable rotor frequency, of the order of 21 cycles per second, for a pipe string frequency of six cycles per second, or less, is readily attainable. As will be seen from an inspection of the drawings, and considering each pair of diametrically opposed rotors separately for the moment (FIGS. 4 and 4a), the eccentric rotor masses 67 of each such pair are so phased as to approach and recede from one another in unison. These eccentric or unbalanced masses 6'7, turning about the axes of planet gears 61, exert centrifugal forces, the reactions of which are exerted on the spool disks 5t) and 51. Owing to the described and illustrated phasing of the unbalanced rotor masses of the rotor pair under consideration, reaction force components r in the direction of a line intersecting the axes of rotation of the two rotors, while the rotors are passing through the position of FIG. 4a, are, accordingly, balanced out. On the other hand, alternating reaction force components I exerted by the two unbalanced rotors 67 along direction lines at right angles to the line intersecting the respective axes of rotation are opposed, but exerted on the opposite side of the longitudinal center line or axis of the spool and, therefore, coact to create an alternating or oscillatory couple, i.e., an oscillatory torque exerted on the rotating spool. It will further be seen that the two pairs of diametrically opposed rotors are phased such that their torque reactions are in phase. The resultant oscillatory torque is exerted through the rotating spool and the tubular extension 32 thereof on fluid impelling means 3% and the pump tubing 15 above. This oscillatory torque angularly oscillates the fluid impelling unit 30 and the elastic pump tubing 16 during and by virtue of the rotation of the pump tubing 16 and of fluid impelling unit 3%. The fluid impelling unit 30! angularly oscillates bodily, but the angular oscillation of the tubing is by virtue of elastic torsional deformation, in one direction and then the other.

In service, of course, the well fluids enter into casing fit through inlets l2 and rise therein to and above the fluid impelling unit 349. These fluids gain entrance into unit 3t) through inlet ports 72 formed in tubular member 32 immediately below unit 39, and thus rise to the vanes 43, which propel the fluid upwardly as previously described. V I

In FIG. 12 is depicted a standing Wave diagram of a sonic pump of the prior type, wherein oscillations are generated at the ground surface, are transmitted down the well as elastic waves (either longitudinal or torsional) in the pump tubing, and vibrate one or a number of fluid impel-ling means in the tubing, such as the aforementioned means 30. The diagram, which represents the standing wave pattern for the full length of the pump tubing, shows the most favorable condition possible to this older sys tem, operating at standing wave resonance, attained by adjustment of the driving frequency until standing waves are attained in the tubing. The wave pattern of FIG. 12 shows by its width the vibration amplitude along the pump tubing, from the ground surface to the lower end. Velocity antinodes (regions of maximized vibration amplitude) are designated at V, spaced by half wave length distances along the tubing. Theoretically, true velocity nodes are experienced at quarter wave length distances from the antinodes. It will be understood that a standing wave, with nodes and antinodes, results from an elastic wave, of proper resonant frequency, being transmitted along an elastic column, and reflected from the end of the column, so that the transmitted and reflected waves interfere, reinforcing one another at certain points called antinodes, and cancelling one another at other points called nodes. In practice, in the sonic pumps, the tubing is so long, and is subject to such damping, that the downwardly advancing wave is gradually attenuated, as is the upwardly reflected wave. Also, the upwardly reflected wave is of lower amplitude, at any given point along the tubing, than is the downwardly advancing wave at that point. The result is that the reflected wave never quite equals the advancing wave at any given point, so that wave cancellation is not attained in practice. True nodes are not obtained for this reason, but so-called pseudo-nodes, with varying degrees of cancellation, are obtained, as designated at P-N in the diagram. It will be noted that the pseudo-node P-N most closely approximating a true node is the lowermost one. Owing to attenuation, the pseudonodes depart more and more from true nodes in the upward direction, as indicated. It will also be noted that owing to attenuation of both the advancing the reflected waves, the vibration amplitude of the Wave gradually decreases in the downward direction. Accordingly, the wave or vibration amplitude A at the lower end of the pump tubing, where pumping effort is most important, is actually at its minimum. Moreover, the several pseudonodes next above the lowermost one are also fairly close approximations of a true node, and vibration amplitude thereat, and for substantial distances up and down therefrom, is relatively small. It is thus evident that the optimized location of fluid impelling units 30, at points of maximized, or large, vibration amplitude in the lower portion of the tubing, say the lower several hundred feet thereof, presents a problem. Difficulty is encountered in placing suflicient such units, and locating them where they will have suflicient oscillation amplitude.

In FIG. 13 is shown a typical standing wave such as may be obtained with the pumping system of FIGS. 1-4, as heretofore described, i.e., Without certain later described wave reflectors. It will be understood that this standing wave is obtained by rotating the tubing at such a rate as will cause the torsion oscillator to generate torsion waves at the resonant frequency for torsional standing waves in the tubing. This resonant frequency may be readily calculated, but is easily found by varying the frequency until the high vibration amplitude manifestations of resonance are apparent. It will be noted that the standing Wave of FIG. 13 is the exact vertical inversion of that of FIG. 12 representing an earlier sonic pump. And, here, the pseudo-nodes P-N most nearly approach true nodes at the top, where pumping efiort is not so important. Wave amplitude B is greatest at the bottom, next to the oscillator, where maximum pumping eflort is most important. The improvement shown in FIG. 13 over the performance indicated in FIG. 12 is quite obvious, attention being directed to the fact that the wave or vibration amplitude B for the pump diagram of FIG. 13 exceeds the amplitude A for the diagram of the prior pump of FIG. 11, and to the further fact that the pseudo-nodes P-N near the bottom also have large vibration amplitudes, meaning the ability to use substantial numbers of fluid impelling units 3% in the lower region of the well, with assurance that good vibration amplitude will be found at each of such units. The pumping system of the invention, in this form, is particularly suited for wells yielding good production from relatively shallow depths.

Material improvement over the situation represented in FIG. 13 is possible, however, by adding means for preventing the torsional vibration from travelling entirely up the pump tubing, which causes considerable loss of energy. To this end, and as shown in FIG. 1, I mount on or incorporate in the pump tubing string 16, at a selected height above the fluid impelling unit 30, a bored wave reflecting inertia mass 75. This may be a long and massive member, for example, feet in length and 8 inches in diameter. As a first example, this inertia mass 75 may be located approximately a quarter wave length distance up the tubing 16 from the lower end of the vibratory system, giving a quarter wave length standing Wave, as diagrammed in FIG. 14'. This quarter wave length distance is found by dividing the speed of propagation of the torsional wave in the tubing 16 (which can be found in standard handbooks, and is approximately 11,000 feet per second) by four times the frequency of the torsional oscillation established. Assuming a torsional oscillation frequency of 21 cycles per second, the quarter wave length distance is 136 feet. A quarter wave length resonant torsional standing wave is thus established in .a 130 foot length of tubing 16 below the inertia wave reflector '75. A velocity antinode V of this torsional standing wave, i.e., a region of maximized torsional vibration amplitude, occurs at the lower end of this quarter wave length of tubing 16, or, in other words, at or near the lowermost fluid impelling unit 30, and the vibration amplitude C at this antinode is quite large-substantially larger than amplitude B of FIG. '13. A nearly true velocity node N (a region of zero or minimized vibration amplitude) occurs at the upper end of the quarter wave length pipe section, i.e., at the inertia mass 75. A condition of standing wave resonance is thereby attained, with large torsional vibration amplitude attained at the fluid impelling unit 30, as is desired for high rate pumping. In the establishment of this standing wave, the inertia mass acts as a reflector of the upwardly propagating torsional wave, the oncoming and the reflected waves combining to produce the desired resonant quarter wave length standing wave, as will be well understood by those skilled in the art of acoustics. A number of the torsional fluid impelling units 30 may in this case be used within the lowermost quarter wave length of the tubing. These units, of course, become less and less eflective as the nodal condition at the reflector 75 is approached. If desired, an additional inertia mass, such as 75a in FIG. 1, may be used at a quarter wave length distance above the described inertia mass 75, and will serve to further isolate the pump tubing string above from the torsional vibratory action at the lower end.

Actually, the distance up the pipe string to the reflective mass 75 can be, any odd multiple of quarter wave lengths, and FIG. 15 is a representative of a modification in which anumber (odd) of quarter Wave lengths has been used. Thus, the wave pattern, up to the reflective mass75, may be several hundred or several thousand feet in length. Substantially a true node is obtained at the reflector, but beginning at the bottom, the odd quarter wave points are pseudo-nodes of substantial vibration amplitude. Thus a large number of fluid impelling units 30 may be installed in the pipe string in the stretch between the lower end of the string and the reflector 75many more than can begaccommodated within the quarter wave length distance represented by FIG. 14. The system of FIG. 15, because of some attenuation up to the reflector, has a vibration amplitude D at the bottom which is not quite as great as that of the quarter wave system of FIG. 14; but the capacity for additional fluid impelling units 3% below the reflector more tahn compensates for this disadvantage. On the other hand, the system of FIG. 15, While not accommodating so many valves as that of FIG. 13, has better vibration amplitude, and still accommodates an adequate number of fluid impelling units 30. The system of FIG. 15 is deemed to optimize various conflicting factors for a deep, high production well.

Referring now to FIGS. 5 and 6, showing a form of my invention utilizing longitudinally oriented vibrations, numeral designates a usual casing extending down the well and formed at its lower end with inlet openings 80a for 'well pnoduction fluid. Casing 30 has at the top a casing head 81, and it is to be understood that casing head 81 and the parts thereabove are the same as shown in more particular in FIG. 2. Thus, an elastic pump tubing string 82 will be understood to be vertically and rotatably supported within casing head 81, and to be continuously rotated by means of pulley 83, belt 84, and pulley 85 on the shaft of motor 86. At the top of tubing string 82 is swivelled outlet fitting 87.

Tubing string 82 containsor is made up of a number of tubing string stands 90, made of longitudinally elastic material, such as steel, and connected by couplings 91. Certain of these couplings 91 contain vibratory fluid impelling means 92 such as shown in FIG. 6. As there shown, the coupling 91 includes a collar 93 screwed in this case onto the threaded end of a standard length of tubing above, and a very short tubing length 90a below. A downwardly diverging tubular member 94 forms at the top a seat for a check valve ball 95, and has at the bottom an outwardly extending annular flange 96 seating on the upper extremity of the tubing length 90a below. At the same time, the lower extremity of the tubing length 90 above engages the somewhat conical exterior surface of member 94, and thus firmly secures the member 94 in position. Check valve ball 95 is caged by a suitable transverse strap 9% supported from member 94.

Well fluids which have entered into casing 8% gain access into the lowermost tubing length 90 by Way of inlet ports 99 formed near the lower end of the tubing string.

The lower, male coupling 1011 on the lower end of the tubing string is engaged Within the female coupling 162 on the upper end of a stem 103 rotatably fitted in the upper end plate 104 of the housing of a longitudinal vibration generator generally designated by numeral 1195. The housing of this generator includes a tubular side wall or barrel 1116 screw-threaded to upper end plate 104, as at 197, and a lower end wall 1% formed integrally with barrel 106 and provided with a threaded coupling socket 199% to receive the threaded upper end 110 of a downwardly projecting stem 111. Surrounding barrel 106 is a sleeve 112, the purpose of which is to enclose certain later described bearings.

The lower end of stem 103 is formed with a threaded socket 115 which receives the threaded upper end of a drive shaft 116 on whose lower end is a bevel pinion 117. The shaft 116 is supported by means of conical roller thrust bearings 118 and 119, in the arrangement clearly shown in the drawing. Pinion 117 meshes with a bevel pinion 120 on a transverse shaft 121 journalled in suitable bearings carried by barrel 106, and on shaft 121 is a relatively large spur gear 122 meshing with a smaller spur gear 123 on a transverse shaft 124 mounted below shaft 121 in bearings carried by barrel 106. Shaft 124 also mounts a large spur gear 125.

Below gear 125 are four spur gears 126, the uppermost meshing with spur gear 125, and each meshing with the gear next below, in the arrangement shown. These spur gears 126 are all mounted on transverse shafts 127 journalled in barrel 106, and each has integrally formed therewith an unbalanced mass 128. That is to say, the mass elements 128 are concentrated off-center or eccentric of the shafts 127. A series of unbalanced rotors is thus provided, with alternate rotors turning in reverse directions. The rotors are so phased that their unbalanced masses 128 move vertically in unison, so that the vertical components of the reactive forces exerted thereby through the shafts 127 on the housing barrel 106 are additive. On the other hand, because of the contrary directions of rotaion of successive rotors, the lateral components of unbalanced forces are cancelled. In operation, therefore, rotation of oscillator drive shaft 116 produces a vertically oriented alternating reactive force on the somewhat massive oscillator housing. This vertical alternating force is in turn exerted by the oscillator housing on the lower end of the tubing string, as more fully explained presently.

Below the oscillator, the downwardly extending stem 111 is received and splined within a bore 135 in an annular inertia body 136, the spline being indicated at 137. A counterbore 138 in body 136 slidingly accommodates an enlarged head 139 on the lower end of shaft 111, and a coil spring 140, which serves to yieldingly support the body 136 from stem 111. The body 136 is provided with bow spring anchors 142 in frictional engagement with the wall of the casing, and which serve to frictionally anchor the body 136 so as to counteract or resist the power torque of the rotating pipe string.

Vertical oscillation of the oscillator housing relative to the anchored body 136 is permitted by the spline at 137.

Considering now the upper end portion of the oscillator, it will be noted that barrel 1% is formed just under the outer race ring of bearing 119 with a shoulder 150,

so that outer race ring of the bearing 119 is vertically supported by the barrel of the oscillator housing. In turn, the outer race ring of bearing 11% is supported by the outer race ring of bearing 119, and the inner race ring of 118 engages directly under the lower extremity of the stem 163 on the lower end of the pipe string. Accordingly, the vertical alternating force generated by the unbalanced rotors of the oscillator and exerted thereby on the housing of the oscillator are applied through the coupling stem 1113 against the lower end of the rotating pipe string. Because of the relatively large mass of the oscillator housing, the alternating force exerted thereby is relatively large, though the vertical velocity amplitude of the resulting vibration, and, of course, the amplitude of the vertical vibratory displacement of the oscillator housing, is relatively small. This condition of high alternating force and low velocity amplitude is one known as high impedance, and a vertical vibratory force at high impedance is thus exerted on the lower end of the rotating pipe string. Waves of alternating compression and tension are thereby sent up the tubing string, and the tubing string above the oscillator vibrates elastically.

The fluid impelling means 92 contained within the lowermost pipe coupling 91 and in additional pipe couplings above are thereby set into vertical oscillation, and pump fluid upwardly in the pipe string in accordance with principles disclosed fully in my aforesaid issued Patent No. 2,444,912. Briefly, the member 34 of each check valve comprises an oscillatory fluid impelling memher. On each downstroke of the vibrating check valve assembly, the check valve ball separates from its valve seat owing to the fact that the valve seat descends with an acceleration greater than that of gravity. Fluid within the member 9'4 is at this time displaced by the down 'ward movement of the member 94 and forced to flow upwardly therethrough to the region above the valve seat. On the succeeding up stroke, the valve ball 95 seats, and the fluid column above the check valve is propelled with considerable kinetic energy. In the specific design of check valve shown in FIG. 6, the fiuid displacing function of tubular member )4 depends upon its generally conical form and the downwardly facing area thereply to the pump of FTGS. 5 and '6 the same as to the pump of FIGS. 1-4, and the diagram of FIG. 13 brings out the advantages of the pump of FIGS. 5 and 6, as so far described, in the same manner as it does the advantages of the pump of FIGS. l4.

To prevent transmission of the elastic waves sent up the tubing string by the alternating force applied thereagainst from travelling all the way up the tubing string, and thereby be subject to substantial attenuation and energy loss, and to conserve this energy and establish a resonant operation, a wave reflecting means similar to what was described in connection with the embodiment of P168. 1-4 is preferably included in the tubing string. Thus, such a wave reflecting means may be used at a quarter wave length distance up the tubing string from the oscillator. The quarter wave length distance is in this case found by dividing the speed of propagation of a longitudinal wave in the elastic tubing, using a handbook value for the speed of sound in the material of the tubing, by four times the frequency of the wave in the tubing (or of the applied alternating force). Thus, at a quarter wave length distance up the tubing from the oscillator, there is mounted on the tubing a wave reflecting inertia mass 144. The result is then that the elastic wave launched upwardly in the tubing by the alternating force impulse applied by the oscillator is reflected at the quarter wave length point and returned downward, acting to reinforce the upwardly launched wave to the maximum extent at the lower end of the tubing and to cancel it at the quarter wave point. A quarter wave length standing Wave is thus set up in the tubing, with a velocity node at the reflector, and a velocity antinode at the lower end of the tubing, as diagrammed in FIG. 14. The fluid i-mpelling unit 9 2 is thereby vibrated with a resonantly augmented amplitude. Additional such units may be crowded in the tubing in the lower portion of the lower quarter wave length, as explained earlier in connection with FIGS. 14 and 14. If desired, an additional wave reflecting inertia mass, such as 144a, may be used at a quarter wave length distance above the described inertia mass 145, serving to further isolate the pump tubing string above from the longitudinal vibratory action at the lower end.

Here, again, as with the embodiment of FIGS. 1-4, the wave reflecting means 144 can be located an odd number of quarter wave lengths up the pipe tubing from the lower end, as also represented by the diagram of FIG. 15, and with advantages the same as explained heretofore in connection with FIGS. -'l 4 and 15.

'FIGS. 7 and 8 show somewhat diagrammatically a modification of the embodiment of FIGS. and 6, wherein the down-hole oscillator is driven from a down-hole electric motor, instead of being driven through a rotating tubing string. In this case, therefore, the tubing string, identified at 82a, is non-rotatable. The casing 80a is shown to be provided at the top with a casing head 81d passing the tubing, and carrying coil springs 145.

which support a platform 146, which, through a tubing coupling 147, yiel-dingly supports the tubing string 82a, accommodating vertical oscillation of the latter in the event that Wave reflectors are not used in the tubing string.

The oscillator 1115a is similar to that of FIGS. 5 and 6, and the internal details need not be again illustrated. The stem 111a at the bottom, with its head 139a, are also as in FIG. 6. In FIGS. 7 and 8, stem 111a projects through and is sp-lined in a bore in the coverplate 150 of a barrel 151, Whose bore accommodates head 139a for free vertical movement therein, and whose lower end has an end Wall 152. Below barrel 151 is an electric drive motor 154, equipped with bow spring anchors 155 for frictional engagement with the casing in order to resist rotation of the motor housing. The drive shaft 156 of the motor is flange-connected to the lower end :wall 152 of barrel 151, as shown. Compression springs 157 and 158 yieldingly center head 139a Within the barrel.

The electric motor is provided with power transmission means in the form of a power supply cable 159 extending to the ground surface, and provided with a suitable leak-tight fit (not shown) through casing head 81a.

The tubing string between the oscillator and the casing head may be as in 'FIG. 5, optionally but preferably incorporating inertia wave reflectors 144 and 144a such as described in connection with FIG. 5.

-In operation, motor 154 is energized, and rotates barrel 151. Barrel 151 in turn rotates the housing of the oscillator. Reference being had to FIG. 6 for the internal details of the oscillator, oscillator shaft 116 and its gear 117, being coupled to the now non-rotating pipe string, in this case does not rotate, and the oscillator housing and gear 120, as well as all of the remaining gear mechanism within the oscillator housing, rotate around the shaft 116 and gear 117. It will be seen that under these conditions, a vertical alternating force is developed as before, and the oscillator oscillates bodily in a vertical direction, so as to generate vertical elastic waves in the pump tubing.

These waves may form any of the patterns shown in FIGS. 13, 14 and 15, depending upon whether an inertia wave reflector is used in the tubing string, and upon its location.

Attention is directed to the use of the spring mounting of the tubing on the casing head, as seen in FIG. 7. It will be understood that the tubing will be slidably packed within the casing head to accommodate vertical 'wave motion of the tubing without vibrating the casing head. The spring mounting shown facilitates the location of a velocity antinode at the top of the tubing, and is useful when wave reflectors are not used in the tubing. Such a spring mounting for the tubing is also useful in the pump of FIGS. 5 and 6 for the case in which wave reflectors are not used in the tubing. Otherwise, the casing head and casing are subject to considerable vibration, and may bleed away substantial energy.

FIG. 9 shows a modification of the torque impulse drive pump of FIGS. 1-4, wherein a down-hole electric motor 170 serves as the prime mover for a torsional oscillator 171. Here, the tubing string 82b is again torsionally elastic, and may be exactly like that of FIGS. 1-4 excepting that it is not rotatable, and excepting for a structural modification in the coupling to the oscillator. The casing 80b may have a conventional casing head, not shown, in which the tubing is packed either for torsional oscillation, or, in case reflectors are used in the tubing, without accommodation for oscillation.

At the lower end of the tubing string 82b is a torsional fluid impel'ling unit Btlb, which may be like the unit 31) of FIGS. 14, and coupled into the lower end of unit 3% is a short pipe 172 having fluid inlet ports 173, and a flange 174 secured to the top of torsional oscillator 171.

Below oscillator 171 is the electric drive motor 170, equipped with bow spring anchors 176 for frictional engagement with the casing in order to resist rotation of the motor housing. The drive shaft 177 of the motor is coupled to an oscillator drive shaft 178, which is journalled in the bottom wall of the oscillator housing. On the inner or upper end of this shaft 178 is a spur gear 179, which meshes on opposite sides with a pair of spur gears 180 driving a corresponding pair of eccentrically weighted rotors 181. The rotors 181 contain bearings which rotatably mount them on stub shafts 182 projecting from the upper wall of the housing. As will be seen, the eccentrically weighted rotors are formed with masses displaced to one side of their axes of rotation, and the two rotors are so phased that these unbalanced masses approach and recede from one another in unison. Forces in the direction of a line intersecting the axes of the two rotors are accordingly balanced out. On the other hand, alternating force components exerted by the two unbalanced rotors along direction lines at right angles to the line intersecting the rotor axes are opposed, but exerted on opposite sides of the longitudinal center line or axis of the oscillator 171, and therefore co-act to create an alternating or oscillatory couple, i.e., an oscillatory torque. Tlhis oscillatory torque is transmitted to the housing of the oscillator and thence to the lower end of the elastic tubing string 8212, which is thereby subjected to an elastic torsional oscillation.

Operation is otherwise as described in connection with the embodiment of FIGS. 1-4. Wave reflectors such as shown in FIG. 1 are optional, but preferred.

In all cases in accordance with the invention, the elastic oscillations which drive the fluid impelling means are generated in the bottom of the hole, and therefore are unattenuated at the point of drive of the fluid impelling means at the lower end of the pump string. Power may be transmitted down the hole for the drive of the oscillator in various ways in accordance with the invention. In many situations, it is practicable and economic to accomplish this drive mechanically, such as by rotat ing the pump tubing, or by use of a rotating shafit inside the pump tubing. In other cases, it may be preferable to employ an electric motor located in the bottom of the well hole. It will be seen that the problem of wave attenuation along a long pipe string or column, between an oscillator located at the ground surface and a fluid impelling means located at the bottom of the well hole, is avoided, vibration amplitude at the bottom of the tubing is improved, and the capability for advantageous location of the vibratory fluid impelling units is improved.

Reference is next directed to FIGS. 9 and 10, showing a modification of the embodiment of FIGS. 1 to 4, according to which the oscillator or wave generator in the lower portion of the well is motivated by means of a mechanically rotating member driven from the ground surface, but wherein, in contradistinction to the embodiment of FIGS. 1-4, the pump tubing is not utilized for this purpose, and instead, rotation is transmitted via a string of rods, similar to sucker rods, running through the pump tubing. The rod string also bears the oscillatory fluid propelling units.

The Well casing is designed generally at 200, perforated in the region of the productive formation, as at 201, and provided at thetop with a casing head 202. Casing head 202 has an outlet passage 203 extending laterally from a vertical bore 204, and the outer end of bore 203 is threaded as at 204. for connection of a delivery line, now shown. A usual or conventional pump tubing string 295 is threaded at the topv into the bottom of the casing head, so as to communicate with the bore 204 of the latter. It will be understood that this tubing string 205 may be equipped with any conventional tubing guides, not shown, for centering it in the casing.

In the top of easing head 202 is a rotary, conical roller type of bearing 210, the outer race ring 211 of which is seated in the casing head, and the inner race ring 212 of which engages under a rotatable head 214, and embraces a shank 2 15 depending from said head Head 214 is equipped with a pulley 216 adapted to be driven through bel; 217 from the pulley 218 of an electric drive motor 211 The bore 204 in the casing head is sealed at the top by any suitable sealing means such as indicated at 220', which is shown as seated in the casing head and forming a seal with the rotating shank 215.

Suspended from shank 215 is a rod string generally designated by the numeral 224, and understood to be conveniently made up of conventional deep well sucker rods, coupled to one [another as at 225 Intercoupled into the sucker rod string, at selected locations therein, are torsional fluid impelling units 226, generally like the units 30 shown in FIG. 3. These units comprise cylindrical bodies 227, carrying flexible vane elements 228, as described in connection with FIG. 3. The torsional oscillatory fluid impelling unit of MG. 10, however, is mounted somewhat differently from that of FIG. 3. tightly into the bottom of body 277, and a rod 2244b of the string 224 is threaded tightly into the top of body 227. Additional fluid propelling units such as 226-may be incorporated in the rod string above he lowermost one just described, in accordance with the practice previously explained in connection with the embodiment of FIGS. 1-4.

Rod 22401 is threaded into the upper end of the shaft 36a of a torsion oscillator or generator 34a, which may be the same in all material particulars as that shown in FIG. 2 and heretofore completely described in both structure and operation.

In operation, rod string 224 is uniformly rotated by means of motor 219, and uniformly drives the torsion oscillator 34a. The latter, in response to such uniform rotation, generates an oscillating torque, which, in a manner similar to that previously described in connection with FIGS. l4, is exerted on the lower end portion of Thus, a short length of rod 224a is threaded the rod string. The rod string 224- is composed of an elastic material, and this oscillating torque exerted on its tern in the rod string 224, and a pattern like any of those.

of FIGS. 13, 14 or 15 maybe employed. The pattern of FIG. 13 is obtained, as earlier described in connection with FIGS. 1-4 and 13, simply by adjusting the frequency of rotation of the rod string 224 to obtain resonance. The pattern of 13 and 14 are realized, on the other hand, by utilization of an inertia reflector 240 in the rod string, located at a quarter wave length distance up the rod string from its lower end of the case of FIG. 14, and located at an odd number of quarter wave lengths up the rod string for the case of FIG. 15. In case of a wave pattern such as that of FIG. 13, fluid impelling units such as 226 may be incorporated in the rod string at selected positions therein, preferably at velocity antinodes, all the way to the ground surface. In case of FIGS. 13 and 14, the fluid impelling units are located primarily below the inertia reflectors, since wave amplitude the-reaboveis quite small.

A number of illustrative embodiments of the invention have been set forth in the drawings and description. It will be understood, however, that these are merely present illustrative embodiments of the invention, and that various changes in design, structure and arrangement may be made without departing from the spirit and scope of the invention or of the appended claims.

I claim:

1. Deep well sonic pumping apparatus, comprisingz an elastic column having at least a portion thereof in the lower portion of the well, a mechanical oscillator located in the lower portion of the well and coupled to said portion of said column to impart elastic oscillations thereto, driving means for said mechanical oscillator drivingly coupled thereto, and including power transmission means extending from the ground surface down said well to said oscillator, and oscillatory fluid impelling means in the lower portion of the well connected to said portion of said elastic column so as to oscillate therewith and operable by virtue of such oscillation to pump fluid up the well.

2. The subject matter of claim 1, wherein said oscillator includes means producing a longitudinal cyclic force output oriented longitudinally of and applied to said elastic column for generation of longitudinal elastic vibrations in said elastic column.

3. The subject matter of claim 1, wherein said oscil lator includes means producing a cyclic torsional couple acting about the longitudinal axis of said elastic column and applied thereto for generation of torsional elastic vibrations in said column.

4. The subject matter of claim 1, including a wave reflecting inertia mass in said column located at a distance equal substantially to an odd number of quarter wave lengths, including unity, up said column from the lower end thereof.

5. The subject matter of claim 1, wherein said driving means comprises a motor located in the lower portion of the well.

6. The subject matter of claim 1, wherein saidelastic column comprises a pump tubing in the well, said tubing surrounding said fluid impelling means.

7. The subject matter of claim 1, including a pump tubing surrounding said fluid impelling means, and wherein said column comprises a rod string inside said tubing.

8. Deep well sonic pumping apparatus, comprising: an elastic tubing string in the well; a' mechanical oscillator located in the lower portion of the well and coupled to a lower portion of said tubing string to impart-elastic oscillations thereto, driving means for said mechanical oscillator operatively drivingly coupled thereto in the lower portion of said Well and including power transmission means extending down the well from the top to the lower portion thereof, and a fluid impelling means connected to said tubing string so as to oscillate therewith and operable by virtue of such oscillation to pump fluid up the tubing string.

9. Deep well sonic pumping apparatus, comprising: an elastic tubing string arranged for rotation in the well, power means operatively connected to and adapted for rotating said tubing string, a mechanical oscillator in the lower portion of the well having a driving coupling with the lower end of said tubing string to be driven thereby and, in turn, to elastically oscillate said tubing string, and a fluid impelling means connected to said lower portion of said tubing string so as to oscillate therewith and operable by virtue of such oscillation to pump fluid up the tubing string.

10. The subject matter of claim 8, wherein said oscillator includes means producing a longitudinal cyclic force output oriented longitudinally of and applied to said elastic tubing string to generate vibrations oriented longitudin-ally of the tubing string.

11. The subject matter of claim 8, wherein said oscillator includes means producing a cyclic torsional couple acting about the longitudinal axis of the tubing string and applied thereto to generate vibrations oriented torsionally of the pipe string.

12. The subject matter of claim 8, including a wave reflecting inertia mass connected in the tubing string at a distance equal substantially to an odd number, including unity, of quarter wave lengths up the tubing string from the oscillator.

13. The subject matter of claim 8, wherein said driving means comprises a motor located in the lower portion of the well.

14. Deep well pumping apparatus, comprising: an elastic column anranged for rotation in the Well, a prime mover located at the ground surface drivingly connected to said elastic column for rotation thereof, a mechanical oscillator in the lower portion of the well having a driving coupling with the lower end portion of said column to be rotatably driven thereby and, in turn, to elastically oscillate said column, and oscillatory fluid impelling means in the lower portion of the well connected to said elastic column so as to oscillate therewith and operable by virtue of such oscillation to pump fluid up the well.

References Cited in the file of this patent UNITED STATES PATENTS 1,334,935 Holst Mar. 23, 1920 1,989,548 Coberly Jan. 29, 1935 2,444,912 Bodine July 13, 1948 2,553,543 Bodine May 22, 1951 

1. DEEP WELL SONIC PUMPING APPARATUS, COMPRISING: AN ELASTIC COLUMN HAVING AT LEAST A PORTION THEREOF IN THE LOWER PORTION OF THE WELL, A MECHANICAL OSCILLATOR LOCATED IN THE LOWER PORTION OF THE WELL AND COUPLED TO SAID PORTION OF SAID COLUMN TO IMPART ELASTIC OSCILLATIONS THERETO, DRIVING MEANS FOR SAID MECHANICAL OSCILLATOR DRIVINGLY COUPLED THERETO, AND INCLUDING POWER TRANSMISSION MEANS EXTENDING FROM THE GROUND SURFACE DOWN SAID WELL TO SAID OSCILLATOR, AND OSCILLATORY FLUID IMPELLING MEANS IN THE LOWER PORTION OF THE WELL CONNECTED TO SAID PORTION OF SAID ELASTIC COLUMN SO AS TO OSCILLATE THEREWITH AND OPER- 